Vibration damper



March 7, 1939.v A. .1L Bocz 2 Re. 21,022

VIBRATION DAMPER March 7, 1939. A. J. BOCZ VIBRATIVON DAMPER voriginal Filed Aug. 16, 192e 3 Sheets-Sheet 2 1N VENT OR.

March 7, 1939. A. J, BOZ Re. 21,022

VIBRATION DAMPER Original Filed Aug. 16, 1926 3 Sheets-Sheet 3k 56 i lj 61 /74 /a 6 INVENTOR.

Reissued Mar. 7, 1939L VIBRATION DAMPER.

Alexander J. Booz, Detroit, Mich.

Original No. 1,756,898, dated April 29, 1930, Serial No. 129,379, August 16, 1926. Application for reissue September 16, 1937, Serial No. 164,245

3 Claims.

My invention relates to a new and useful balancer and dampener for engines, particularly engines of a type in which reciprocating and rotating parts are associated for the deliverance of '1 power, such as in internal combustion engines and piston operated engines and such other type of mechanism, electric apparatuses, etc.; whose operation effects a setting up of vibration or unbalanced fcrces.-` In the operation of an engine,

10 the vibration at certain speeds is more pronounced, although vibrations always exist during operation. The present invention is to overcome these vibrations and to prevent the accumulation of molecular vibrations for the critical speed.

15 The cause of critical vibrations lies in synchronism at high speeds, between vibration producing impulses and the natural rate of vibration of the shaft. These vibrations are due to the flexibility of the shaft.v All shafts have a certain degree of elasticity, and consequently the shaft is subject to elastic deformations or angular deflections under the application of torque. Since the torque of an internal combustion engine is variable, it follows that the amount of angular deflection accordingly oscillations axially and radially.

When the frequency of the torsional oscillations andthe vibrations of molecules are in accord with thev natural vibration period of the crank shaft,

the deflections are greatly increased, and, thev result is increased vibration. The rear end of the crank shaft, in the ordinary construction of an engine, is restrained from rapid acceleration by the inertia of its flywheel. During rotation'a torsional moment onthe crank shaft is always present,` but is rapidly increased in the immediate vicinity on any of the crank pins at the instant of the explosion in the cylinder. The crank shaft 4 0 will twist slightly, and a moment later, as the torsional eiect on the crank pin decreases, the crank shaft will `unwind owing toits .torsional elasticity. Thereafter, the torsional-force ofanother crank pin `will increase and cause the crank shaft to wind up again. In this torsional vibration there isalso effected an axial movemcntof the crank shaft `as well as a .deflection of the crank shaft from its normal axial position.

I'one cylinder engines there is slight axial vibration because of the shortness of the crank shaft.

' The present invention is adaptable for an engine of .any number of cylinders. v f

In a six cylinder engine, oran engine made up 55 of a multiple of six cylinders, the primary, seovaries upon transmission` of 'this torque to theshaft, thus causing said .shaft to have torsional ondary and fourth harmonic unbalanced forces are canceled but there arises sixth harmonic unbalanced forces as Well as the torsional unbalanced forces and the resonance vibrations.

In an eight cylinder engine, or an engine made 5 up of a multiple of eight-cylinders, the primary and secondary harmonic unbalanced forces are canceled, the'fourth harmonic unbalanced'forces, the torsional vibrations, and the resonance vibration are not dampened.

The present invention has for its 'object the provision of a device with my natural vibrationless means, to balance all the unbalanced forces automatically as well as to dampen vibrations at any speed,` and in all directions in a revolving body. l5

The present invention has also for its object the 'provision of a. balancer, and dampener with my natural vibrationless means, in which a balancing and dampening eiectrisbrought about through radialv and axial operation forcounterbalancing the yradial and axial' forces present during the operation of engines, machines, vitaphones, etc. The invention consists of the combination and arrangement of partshereinafter described and claimed. 25 The invention will bebest understood by a rei--I 'erence to the accompanying drawings which' form a part of this specification andin which,

Fig. 1 is a front elevation view of apart of an engine showing one form of the invention applied with parts in section and parts broken away.

Fig. 2 is a fragmentary sectional 'view taken on substantially line 2-2 of Fig. 1.

Fig. 3 is a fragmentary sectional view'taken "on substantiallyline l-lof Fig. 1. 1 l

Fig. 4 .is a front elevation view of a modified' form of the invention showing itmounted on av shaft, and shown partly in section. l i l Fig. 5 is a fragmentary sectional view taken on substantially 1ine6-6 0f F18. 4. l

Fig. 6 is a perspective view of a ball used in the invention. 4 n

` Fig. 7 is a fragmentary, ction view taken onsub'stantially line 8-8 of Fig. 5.

Fig. 8 is a fragmentary view'taken ony substan- 45r` Fig.' 9 is a front elevational. view of a further modified form of the invention showing it applied to a shaft, and shown in fragment."

Fig. 10 is a fragmentary sectional view taken on 50 substantially line lle-'I I of'Fig". 9.

One form 'of my invention shown in'Flgs. 1, 2, and 3, a crank shaft I9 projects throughthe front wall 20`of' a'housing 2|,` which is positioned forv ward of the timing `gear housing '22, the usual 55 timing gears 23 and 24 being shown. Fixedly mounted upon the crank shaft I9, to rotate therewith is a collar 25, on one side of which is an arm 26, the collar and arm serving to form a bracket or carrying member rotatable with the crank shaft. Fixedly mounted in the bracket is a plug 21, having a head 28, in which is formed a concave depression or pocket 29. Projecting outwardly adjacent to the end of the arm 26 is a stud 38, which is threaded for the reception of the suitable nut 3 I. A similar stud 32 projects outwardly from the bracket at the opposite end, this stud 32 being also threaded for a nut 33. A counteracting ordampening inertia mass 34, used in this invention, may be termed a displaceable inertia mass, being provided with much large holes 34', for projecting studs 30 and 32 therethrough so that there is always a clearance between the studs and holes. Said displaceable inertia mass is provided with spherical contact member 35. Recesses 36 and 31 are formed in the opposite sides of said inertia mass to engage the ends of the springs 38 and 39. The opposite ends of said springs are held in cups and 4I, to overcome any displacement of the. center-line of said springs and to prevent the natural vibration of the springs, to overcome the resonance vibrations, and to increase the resistance of the springs to respond to vibrations at all speeds. Through this arrangement or like manner by preventing any displacement of said springs the natural vibrations of the studs 31| and 32 are also dampened. The springs 38 and 39, and

cups 48 and 4I, are retained in position by means of nuts 3| and 33or other means, for instance by rivets.

It is evident that turning the nuts 3| and 33 will change the pressure oi' the springs 38 and 39, so thatthe inertia mass 34 isalways displaceable therebetween on its contact point 35, which point may be varied. The structure is such, that the inertia mass 34 may be displaced on its contact point 35, against the resistance of either of the springs 38 and 39. A swinging longitudinally of the inertia mass 34 effects an additional compression to the spring 38, and a swinging of said mass inv another longitudinal direction puts an additional pressure to the spring 39. 'I'he said inertia mass may also be displaceable transversely on its contact point 35, which point varies, and induces an additional force upon said inertia mass to be transmitted to the springs 38 and 39 under normal/ conditions.

It will be noted in'Fig. 1, that one side of said inertia mass is positioned a greater distance from the center-line of its rotation, than the opposite side. so that said inertia mass will be slightly tilted on its contact point 35. As the various unbalanced forces and` vibrations are transmitted through the crank shaft I9, to the natural vibrationless springs 38 and 39, the state of inertia of said mass,.with the co-operation of the springs will concentrate, neutralize, dampen, and oppose the unbalanced and vibrating forces of the crank shaft I9.

In operation the inertia mass 34 is held in its plane of rotation by the natural vibrationless springs 38 and 39, which springs respond to the torsional vibrations, said vibrations tending to displace the center-line of the revolving shaft I9, either through whipping, twisting, or bending said shaft or any other way striving to move the center-line of said shaft out of its plane of rotation. Since the inertia mass 34 is held by said natural vibrationless springs in its plane of rotation, and said springs are so connected to the carrying member to revolve with the shaft I9. Therefore the inertia mass will concentrate, neutralize and oppose said forces in its plane of rotation.

In the form shown in Figs. 4, 5, 6, 7, and 8, the same forces are applied for balancing and v.dampening as were called into play in the device as described and illustrated with Figs. 1, 2, and 3. 'I'he revolving part of the shaft I9 has a collar 42, which is connected to the blocks 43 and 44 by meansv of screws 45 and 46. These screws serve to bind the collar on the shaft I9' and to rotate therewith. An engagement member 41, which formed arcuately at its ends for connecting the ends of the screws 45 and 46, and one end of the coil springs 48 and 49 on which they are located and squared, so that misalignment of the ends of said springs is prevented.

As shown in Fig. 5 the revolving part of a shaft I9' projects through the gear 24, anda stud 58 is ilxedly mounted thereon. A lock ring 5I is attached to said stud, which ring is positioned in an opening 52, which is formed in the inertia masses 54-and 54', vsaid masses comprising the reduced portion 53 and 53. The thicker portions 54 and 54' are provided with pockets 55 and 55', and in these pockets the other ends of the springs 48 and 49 are squared and guided against any displacement of their center-lines. The reduced portions 53 and 53' overlap each other, which is clearly shown in Fig. 4. 'I'hese are mounted on the lock ring 5I and are held together by a flexible clip 52', said clip is retained in position by means of a notch 52, or other means; thus a universal movement oi.' said is attained against the compression or tension of the springs 48 and 49. Axial movement is also insured for said masses against the resistance of said springs, because the lock ring 5I is slidable on the stud 58; any or all of these movements are limited and resisted by the natural vibrationless y springs, One method to control the natural vibrations of exible means has been described and illustrated by Figs. 1, 2, and 3.

W'hen the said part revolves with the inertia masses 54 and 54', these masses are in their plane of rotation at right angles to the axis of said part, and are capable of swinging universally, and at the same time capable of an independent radial motion. All of these movements are limited and resisted by the springs, whose natural vibrations are prevented and dampened, so that thetorsional and other vibrations are concentrated, neutralized, and dampened in their plane of rotation.

In Figs. 9 and 10, I have shown a further modied Vform of my invention,V in which `there is mounted flxedly upon a revolving part of a shaft I 9', a ring 56, and an arm 51 projecting therefrom, forming a bra ket, through which the bolt 53 extends, and is positioned between a pair of lugs 59 and 58, and ektending from the inertia mass 5I.

A bolt 584s positioned in the core of the coil springs 62` and (i3.V The ends of said springs are squared and guided, to prevent any displacement of said springs, tc minimize the defection thereof. So that the natural vibrations of said springs are dampened.

The said lugs are positioned between the other ends of the springs G2 and 63, the pressure or tension `of these springs on the lugs 59 and 39 being determined by nuts 64, which is on thc bolt 53, with or without washer 64'.

lock ring 65, so as to have a universal movement thereon, this lock ring being positioned on a stud 66, which projects from one side of the gear 61. Therefore said inertia mass is movable radially as well as universally at the same time.

When thesaid part rotates with the shaft I9', the arm 51 will rotate in unison therewith as will also the gear 61, carrying with it the mass 6|. When the impulses of the vibrating forces are transmitted to the inertia mass 6I, through the natural vibrationless springs 62 and 63, said mass has all direction movements between said springs in its plane of rotation. The direction of these displacements is dependent upon the direction in which the forces are transmitted and the nature of the vibrating forces, which are being concentrated, neutralized, dampened, and minimized with the resistance of the inertia mass GI and the spring Vcontrolled means; so that said controlled means will resist any orali vibrating forces at all speeds.

With the various forms illustrated, the advan? tages and features of my invention are believed shown in a manner practically adaptable to engines of various types. A practical and simple method is illustrated for overcoming the unbalanced harmonic forces, and torsional vibrations and such other vibrating forces as may exist in any engine, machine, Vitaphone, etc., where it is desirable to reduce such vibrations and other vibrations with the natural vibrationless flexible means.

Itis understood that the assembled device must tions and modications as may come within the claim as new and desire to secure by-Letters Patent is:

' 1. A vibration damper for a shaft consisting of a supporting member adapted to be secured to said shaft, radial spaced rod elements thereon, a

,spherical concave seat mounted on said supporting member intermediate said rod elements and eccentric to its axis of rotation, a displaceable inertia member having apertures of much larger diameter than that of the rod elements passing therethrough, a spherical convex projection secured to said inertia member and abutting said lconcave seat, retaining means on said rod elements and natural-vibrations-controlled resilient means between said inertia member and retaining means for connecting the spherical convex projection to said concave'seat.

2. `A vibration damper for a shaft consisting of a supporting member adapted to be secured to said shaft, radial spaced rod elements thereon, a lspherical concave seat mounted on said supporting member intermediate said rod elements and eccentric to its axis of rotation, a displaceable inertia member having apertures of much larger diameter than that of the rod elements passing therethrough, a spherical convex projection secured to said inertia member and abutting said concave seat, retaining means on. said rod elements and,natural-vibrations-controlled resilient means for connecting said inertia member and retaining means, to limit the axial and radial displacements of said convex projection on said concave seat.

3. A vibration damper for a shaft consisting of a supporting member adapted to be secured to said shaft. radial spaced rod elements thereon, a spherical concave seat mounted on said supporting member intermediate said rod elements and eccentric to its axis of rotation, an inertia member displaceable axially and radially thereon, having apertures of much larger diameter than that of the rod elements passing therethrough, a spherical convex projection secured to said inertia member and abutting said concave seat, retaining means on said rod elements and natural vibrations controlled resilient means between said inertia member and retaining means for connecting said convex projection to said concave seat.

ALEXANDER. J. Booz. 

